US20180209447A1 - Centrifugal Pump Blade Profile - Google Patents

Centrifugal Pump Blade Profile Download PDF

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Publication number
US20180209447A1
US20180209447A1 US15/745,635 US201615745635A US2018209447A1 US 20180209447 A1 US20180209447 A1 US 20180209447A1 US 201615745635 A US201615745635 A US 201615745635A US 2018209447 A1 US2018209447 A1 US 2018209447A1
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United States
Prior art keywords
profile
blade
centrifugal pump
angle
intake
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Abandoned
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US15/745,635
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English (en)
Inventor
Peer Springer
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KSB AG
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KSB AG
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Filing date
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Assigned to KSB AKTIENGESELLSCHAFT reassignment KSB AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SPRINGER, PEER
Publication of US20180209447A1 publication Critical patent/US20180209447A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/225—Channel wheels, e.g. one blade or one flow channel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2277—Rotors specially for centrifugal pumps with special measures for increasing NPSH or dealing with liquids near boiling-point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F04D29/245—Geometry, shape for special effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/72—Shape symmetric

Definitions

  • the invention relates to a centrifugal pump having an impeller which has at least one blade and a method for configuring the profile of a blade of the impeller of a centrifugal pump.
  • the invention further relates to centrifugal pumps which are used to convey media containing solids.
  • channel type impellers, free-flow impellers or single blade impellers can be used as impellers.
  • Ducted wheels are open or closed impellers with a reduced number of blades.
  • One, two or three blades in radial and semi-axial impellers have been found to be advantageous.
  • the fields of application thereof are liquids which are silted up or loaded with solid materials.
  • the ball passage is also referred to as a free, unnarrowed impeller passage and describes the largest permissible diameter of the solid materials in order to ensure a blockage-free passage.
  • the single blade impeller produced using a casting method forms between a front cover plate and a rear cover plate a channel whose cross-section decreases from the intake of the single blade impeller toward the discharge.
  • the intake side forms on the first 180° of the rotation angle a semi-circle which is arranged concentrically with respect to the rotation axis.
  • the single blade impeller is constructed in such a manner that an occurrence of cavitations is reduced.
  • impellers with a plurality of blades are distinguished by a higher degree of efficiency.
  • specific requirements are also placed on such impellers in terms of preventing deposits of solid components in the conveying channel.
  • specific measures have to be taken to prevent blockages.
  • centrifugal pumps with high specific speeds are increasingly used. With conventional impellers, this results, in the event of a blade being subjected to flow, in the stagnation point thereof, in particular during partial load operation, moving to the pressure side of the blades.
  • the intake edges of the blades are flowed around from the pressure side to the intake side.
  • the stagnation point located at the pressure side presses fibers located in the waste water onto the surface of the blades.
  • the high speed region is adjoined by a region of low speed. Dead water is produced at that location. Fibers which adhere to the intake edge tend to fill this dead water region. As a result of the flow, the fibers are pressed onto the blade contour, wherein the occupation with fibers can increase considerably.
  • DE 10 2011 007 907 B3 relates to an impeller of a centrifugal pump for conveying media containing solid material.
  • the impeller has at least two blades.
  • the blade intake angle is in this instance less than 0°.
  • the blade angle increases in a first portion until it reaches a value of 0°. In a second portion, there is a further increase until a maximum value is reached. In a third portion, the blade angle decreases again.
  • the ball passage, the steepness of the characteristic line, the cavitation properties and the blade loading have a particular relationship in waste water impellers. In contrast to applications for clean water, the ball passage is of central importance.
  • the characteristic line shape is determined by the staggering angle of the blades.
  • the angles at the intake and discharge substantially determine the adaptation of the design to the desired operating location or change the load distribution (pressure difference between blade intake to blade pressure side) along the blade contour.
  • the object of the invention is to provide a centrifugal pump having an impeller in which the loading of the blades is minimized.
  • separation or cavitation regions are intended to be prevented.
  • the formation of dead water regions or return flow regions is also intended to be prevented.
  • the blade has a profile which is produced by superimposing a symmetrical profile with at least one additional profile and a median line whose blade intake angle is less than 0°.
  • a profile ensures uniform loading of the entire blade face.
  • the loading or circulation in this instance is limited to the respective minimum magnitude. Separation or cavitation regions at the intake side are thereby prevented.
  • dead water or return flow regions can be prevented in a selective manner.
  • median line also profile center line or camber line or curvature line
  • the term median line is used to refer to the connection line of the circle center points which are inscribed in a profile. From the projection circle center point to the profile projection, the median line extends in a straight manner. The path of the median line substantially also determines the flow properties. Important geometric characteristic values of the median lines are, in addition to the blade angle, the angle of wrap.
  • the median line which is used for superimposition in this instance preferably has an angle path in which the negative blade intake angle initially increases until it reaches a value of 0. In a second portion, the blade angle then increases to a maximum value and finally decreases again in a third portion. In a preferred embodiment of the invention, the blade angle of the median line remains constant in an adjacent fourth portion.
  • this load variation is carried out with additional profiles.
  • the profiles are varied in each blade calculation step with regard to length and thickness separately at the intake and pressure side in order to reduce the loading and consequently to prevent at the intake side cavitation or separation and at the pressure side dead water or return flow.
  • the desired profile is formed from a characteristic median line, a symmetrical basic profile and additional profiles at the intake side and additional profiles at the pressure side.
  • the symmetrical basic profile is preferably a profile of equal thickness with an elliptical profile projection.
  • the additional profiles can be provided on the basis of catalogue profiles.
  • NACA profiles National Advisory Committee for Aeronautics
  • NACA profiles National Advisory Committee for Aeronautics
  • the superimposition is carried out in this instance in a planar mapping system of the Kaplan method.
  • the profile shapes according to the invention are produced by the superimposition of the characteristic median line which has a negative blade intake angle, together with a thickness distribution or a profile droplet.
  • the completed profile is then positioned at the necessary angle of attack ⁇ m in a conformal mapping.
  • the entire blade is produced by conformal mapping of the individual blade portions which are present in the plane in the flood faces which are present as axially symmetrical rotation faces.
  • a sufficiently smooth surface is produced.
  • the provision of the blade profile is preferably carried out by superimposing an asymmetrical profile droplet and the characteristic median line.
  • FIG. 1 is an axial section through an impeller
  • FIG. 2 are plan views of variable droplets on three flow lines
  • FIG. 3 is a meridional section
  • FIG. 4 a shows a path of the blade angle
  • FIG. 4 b is a conformal mapping of the median line
  • FIG. 5 shows a variable region for a thickness variation
  • FIG. 6 shows a profile structure in conformal mapping prior to superimposition with the median line
  • FIG. 7 shows a superimposition profile using the example of an NACA profile
  • FIG. 8 is a conformal mapping of variable droplets on three flow lines
  • FIG. 9 is a perspective illustration of an impeller according to an embodiment of the present invention.
  • FIG. 1 is an axial section through a radial impeller.
  • the liquid which is charged with solid admixtures enters the intake mouth 1 of the impeller.
  • the blades 4 which are arranged between the covering plate 2 and carrier plate 3 accelerate the liquid.
  • the liquid flows radially outward from the rotation axis 5 .
  • the impeller is in particular operated at specific speeds of more than 70 l/min.
  • a low ratio of blade discharge radius R 2 to blade intake radius R 1 is found to be particularly favorable.
  • the ratio of blade discharge radius R 2 to blade intake radius R 1 is less than 1.3.
  • FIGS. 2 a , 2 b and 2 c show variable droplets on three flow lines as a plan view.
  • FIG. 3 shows the three flow lines as a meridional section.
  • FIG. 4 a the path of the blade angle ⁇ is illustrated.
  • FIG. 4 b shows a conformal mapping of the median line.
  • the angle of wrap ⁇ is indicated.
  • the blade angle ⁇ of the median lines is indicated.
  • the blade intake angle ⁇ 1 is less than 0°.
  • the blade angle ⁇ constantly increases until it reaches a value of 0°.
  • a second portion 7 there is produced a constant drive until the blade angle ⁇ reaches a maximum value.
  • the gradient of the increase of the blade angle ⁇ is the same in the first portion 6 and in the second portion 7 .
  • the blade angle ⁇ reaches its maximum value at the turning point of the median line.
  • the blade angle ⁇ constantly decreases until it reaches the value of the blade angle ⁇ 2 .
  • the blade angle ⁇ remains constant at the value of the blade discharge angle ⁇ 2 .
  • the conformal mapping of the median line shows that, starting from the blade radius R 1 , the radius first decreases to a minimum value R min and subsequently further increases up to the value of the blade discharge radius R 2 .
  • FIG. 5 shows a variable range for a thickness variation. As far as a narrowest portion, a region 1 ′ which rises with a decreasing number of blades in which the loading (circulation) can be configured in a variable manner is available. This variable range is indicated as 1 ′ in FIG. 5 . In addition, the angle of staggering ⁇ m is indicated.
  • the load variation is carried out with additional profiles which in each blade calculation step in terms of length and thickness are varied separately at the intake and pressure side in order to limit the loading (circulation) to the respective minimum magnitude and consequently to prevent separation or cavitation regions (at the intake side) and dead water or return flow regions (at the pressure side).
  • FIG. 6 shows a profile structure with conformal mapping prior to superimposition with the median line having a basic profile 10 of the pressure side and a basic profile 11 of the intake side. From the median line and a symmetrical basic profile (identical profile with elliptical profile projection) as well as an additional profile 12 at the intake side and an additional profile 13 at the pressure side, the desired profile is formed.
  • the additional profiles 12 , 13 can be provided on the basis of catalogue profiles, for example, a superimposition profile illustrated in FIG. 7 (NACA 65010).
  • the superimposition is carried out in a planar mapping system in accordance with the Kaplan method.
  • FIG. 8 shows a variable droplet on three flow lines with the conformal mapping. Three blade sections were shown in the conformal mapping forms
  • the optimization of the blade is carried out by adapted configuration and re-calculation methods.
  • FIG. 9 The result of the design is illustrated in FIG. 9 with reference to a dual blade waste water frame.
  • the method can be used for open or closed impellers.
  • the invention relates to a centrifugal pump having an impeller which has at least one blade and a method for configuring the profile of a blade of the impeller of a centrifugal pump.
  • the invention relates to centrifugal pumps which are used to convey media containing solids.
  • channel type impellers, free-flow impellers or single blade impellers can be used as impellers.
  • Ducted wheels are open or closed impellers with a reduced number of blades. 1 , 2 or three blades in radial and semi-axial impellers have been found to be advantageous.
  • the fields of application thereof are liquids which are silted up or loaded with solid materials.
  • the ball passage is also referred to as a free, unnarrowed impeller passage and describes the largest permissible diameter of the solid materials in order to ensure a blockage-free passage.
  • the single blade impeller produced using a casting method forms between a front cover plate and a rear cover plate a channel whose cross-section decreases from the intake of the single blade impeller toward the discharge.
  • the intake side forms on the first 180° of the rotation angle a semi-circle which is arranged concentrically with respect to the rotation axis.
  • the single blade impeller is constructed in such a manner that an occurrence of cavitations is reduced.
  • impellers with a plurality of blades are distinguished by a higher degree of efficiency.
  • specific requirements are also placed on such impellers in terms of preventing deposits of solid components in the conveying channel.
  • specific measures have to be taken to prevent blockages.
  • centrifugal pumps with high specific speeds are increasingly used. With conventional impellers, this results, in the event of a blade being subjected to flow, in the stagnation point thereof, in particular during partial load operation, moving to the pressure side of the blades.
  • the intake edges of the blades are flowed around from the pressure side to the intake side.
  • the stagnation point located at the pressure side presses fibers located in the waste water onto the surface of the blades.
  • the high speed region is adjoined by a region of low speed. Dead water is produced at that location. Fibers which adhere to the intake edge tend to fill this dead water region. As a result of the flow, the fibers are pressed onto the blade contour, wherein the occupation with fibers can increase considerably.
  • DE 10 2011 007 907 B3 relates to an impeller of a centrifugal pump for conveying media containing solid material.
  • the impeller has at least two blades.
  • the blade intake angle is in this instance less than 0°.
  • the blade angle increases in a first portion until it reaches a value of 0°. In a second portion, there is a further increase until a maximum value is reached. In a third portion, the blade angle decreases again.
  • the ball passage, the steepness of the characteristic line, the cavitation properties and the blade loading have a particular relationship in waste water impellers. In contrast to applications for clean water, the ball passage is of central importance.
  • the characteristic line shape is determined by the staggering angle of the blades.
  • the angles at the intake and discharge substantially determine the adaptation of the design to the desired operating location or change the load distribution (pressure difference between blade intake to blade pressure side) along the blade contour.
  • the object of the invention is to provide a centrifugal pump having an impeller in which the loading of the blades is minimized.
  • separation or cavitation regions are intended to be prevented.
  • the formation of dead water regions or return flow regions is also intended to be prevented.
  • centrifugal pump having the features of claim 1 and a method for configuring the profile of a blade of the impeller of a centrifugal pump according to claim 11 .
  • Preferred variants are set out in the dependent claims.
  • the blade has a profile which is produced by means of superimposing a symmetrical profile with at least one additional profile and a median line whose blade intake angle is less than 0°.
  • a profile ensures uniform loading of the entire blade face.
  • the loading or circulation in this instance is limited to the respective minimum magnitude. Separation or cavitation regions at the intake side are thereby prevented.
  • dead water or return flow regions can be prevented in a selective manner.
  • median line also profile center line or camber line or curvature line
  • the term median line is used to refer to the connection line of the circle center points which are inscribed in a profile. From the projection circle center point to the profile projection, the median line extends in a straight manner. The path of the median line substantially also determines the flow properties. Important geometric characteristic values of the median lines are, in addition to the blade angle, the angle of wrap.
  • the median line which is used for superimposition in this instance preferably has an angle path in which the negative blade intake angle initially increases until it reaches a value of 0. In a second portion, the blade angle then increases to a maximum value and finally decreases again in a third portion. In a preferred embodiment of the invention, the blade angle of the median line remains constant in an adjacent fourth portion.
  • this load variation is carried out with additional profiles.
  • the profiles are varied in each blade calculation step with regard to length and thickness separately at the intake and pressure side in order to reduce the loading and consequently to prevent at the intake side cavitation or separation and at the pressure side dead water or return flow.
  • the desired profile is formed from a characteristic median line, a symmetrical basic profile and additional profiles at the intake side and additional profiles at the pressure side.
  • the symmetrical basic profile is preferably a profile of equal thickness with an elliptical profile projection.
  • the additional profiles can be provided on the basis of catalogue profiles.
  • NACA profiles National Advisory Committee for Aeronautics
  • NACA profiles National Advisory Committee for Aeronautics
  • the superimposition is carried out in this instance in a planar mapping system of the Kaplan method.
  • the profile shapes according to the invention are produced by the superimposition of the characteristic median line which has a negative blade intake angle, together with a thickness distribution or a profile droplet.
  • the completed profile is then positioned at the necessary angle of attack ⁇ m in a conformal mapping.
  • the entire blade is produced by means of conformal mapping of the individual blade portions which are present in the plane in the flood faces which are present as axially symmetrical rotation faces.
  • a sufficiently smooth surface is produced.
  • the provision of the blade profile is preferably carried out by means of superimposing an asymmetrical profile droplet and the characteristic median line.
  • FIG. 1 is an axial section through an impeller
  • FIG. 2 are plan views of variable droplets on three flow lines
  • FIG. 3 is a meridional section
  • FIG. 4 a shows a path of the blade angle
  • FIG. 4 b is a conformal mapping of the median line
  • FIG. 5 shows a variable region for a thickness variation
  • FIG. 6 shows a profile structure in conformal mapping prior to superimposition with the median line
  • FIG. 7 shows a superimposition profile using the example of an NACA profile
  • FIG. 8 is a conformal mapping of variable droplets on three flow lines
  • FIG. 9 is a perspective illustration of an impeller according to the invention.
  • FIG. 1 is an axial section through a radial impeller.
  • the liquid which is charged with solid admixtures enters the intake mouth 1 of the impeller.
  • the blades 4 which are arranged between the covering plate 2 and carrier plate 3 accelerate the liquid.
  • the liquid flows radially outward from the rotation axis 5 .
  • the impeller is in particular operated at specific speeds of more than 70 l/min.
  • a low ratio of blade discharge radius R 2 to blade intake radius R 1 is found to be particularly favorable.
  • the ratio of blade discharge radius R 2 to blade intake radius R 1 is less than 1.3.
  • FIGS. 2 a , 2 b and 2 c show variable droplets on three flow lines as a plan view.
  • FIG. 3 shows the three flow lines as a meridional section.
  • FIG. 4 a the path of the blade angle ⁇ is illustrated.
  • FIG. 4 b shows a conformal mapping of the median line.
  • the angle of wrap ⁇ is indicated.
  • the blade angle ⁇ of the median lines is indicated.
  • the blade intake angle ⁇ 1 is less than 0°.
  • the blade angle ⁇ constantly increases until it reaches a value of 0°.
  • a second portion 7 there is produced a constant drive until the blade angle ⁇ reaches a maximum value.
  • the gradient of the increase of the blade angle ⁇ is the same in the first portion 6 and in the second portion 7 .
  • the blade angle ⁇ reaches its maximum value at the turning point of the median line.
  • the blade angle ⁇ constantly decreases until it reaches the value of the blade angle ⁇ 2 .
  • the blade angle ⁇ remains constant at the value of the blade discharge angle ⁇ 2 .
  • the conformal mapping of the median line shows that, starting from the blade radius R 1 , the radius first decreases to a minimum value R min and subsequently further increases up to the value of the blade discharge radius R 2 .
  • FIG. 5 shows a variable range for a thickness variation. As far as a narrowest portion, a region 1 ′ which rises with a decreasing number of blades in which the loading (circulation) can be configured in a variable manner is available. This variable range is indicated as 1 ′ in FIG. 5 . In addition, the angle of staggering ⁇ m is indicated.
  • the load variation is carried out with additional profiles which in each blade calculation step in terms of length and thickness are varied separately at the intake and pressure side in order to limit the loading (circulation) to the respective minimum magnitude and consequently to prevent separation or cavitation regions (at the intake side) and dead water or return flow regions (at the pressure side).
  • FIG. 6 shows a profile structure with conformal mapping prior to superimposition with the median line having a basic profile 10 of the pressure side and a basic profile 11 of the intake side. From the median line and a symmetrical basic profile (identical profile with elliptical profile projection) as well as an additional profile 12 at the intake side and an additional profile 13 at the pressure side, the desired profile is formed.
  • the additional profiles 12 , 13 can be provided on the basis of catalogue profiles, for example, a superimposition profile illustrated in FIG. 7 (NACA 65010).
  • the superimposition is carried out in a planar mapping system in accordance with the Kaplan method.
  • FIG. 8 shows a variable droplet on three flow lines with the conformal mapping. Three blade sections were shown in the conformal mapping forms
  • the optimization of the blade is carried out by means of adapted configuration and re-calculation methods.
  • FIG. 9 The result of the design is illustrated in FIG. 9 with reference to a dual blade waste water frame.
  • the method can be used for open or closed impellers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US15/745,635 2015-07-17 2016-06-23 Centrifugal Pump Blade Profile Abandoned US20180209447A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102015213451.2A DE102015213451B4 (de) 2015-07-17 2015-07-17 Kreiselpumpen-Schaufelprofil
DE102015213451.2 2015-07-17
PCT/EP2016/064605 WO2017012825A1 (de) 2015-07-17 2016-06-23 Kreiselpumpen-schaufelprofil

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US15/745,635 Abandoned US20180209447A1 (en) 2015-07-17 2016-06-23 Centrifugal Pump Blade Profile

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US (1) US20180209447A1 (de)
EP (1) EP3325810A1 (de)
DE (1) DE102015213451B4 (de)
WO (1) WO2017012825A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102416990B1 (ko) * 2022-01-24 2022-07-06 주식회사 일렉트리코 발전 플랜트용 복수기의 세정볼 순환펌프

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL2018044B1 (en) * 2016-12-22 2018-06-29 Ihc Holland Ie Bv Impeller with rotor blades for centrifugal pump
DE102019005469A1 (de) * 2019-08-05 2021-02-11 KSB SE & Co. KGaA Geschlossenes Kreiselpumpenkanallaufrad für Flüssigkeiten mit abrasiven oder erosiven Beimengungen
DE102021118564A1 (de) 2021-07-19 2023-01-19 KSB SE & Co. KGaA Schaufelanordnung mit Mikroschaufeln

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4063849A (en) * 1975-02-12 1977-12-20 Modianos Doan D Non-clogging, centrifugal, coaxial discharge pump
JPS59192898A (ja) * 1983-04-15 1984-11-01 Hitachi Zosen Corp 遠心羽根車
CH672532A5 (en) 1987-01-29 1989-11-30 Sulzer Ag Impeller for centrifugal pump - has blade angle profile chosen to minimise danger of cavitation
DE4015331A1 (de) 1990-05-12 1991-11-14 Klein Schanzlin & Becker Ag Einschaufelrad fuer kreiselpumpen
DE102010027588A1 (de) * 2010-07-19 2012-01-19 Rolls-Royce Deutschland Ltd & Co Kg Fan-Nachleitradschaufel eines Turbofantriebwerks
DE102011007907B3 (de) 2011-04-21 2012-06-21 Ksb Aktiengesellschaft Laufrad für Kreiselpumpen
EP2711557B1 (de) * 2012-09-20 2019-10-02 Sulzer Management AG Flügelrad für eine Zentrifugalpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102416990B1 (ko) * 2022-01-24 2022-07-06 주식회사 일렉트리코 발전 플랜트용 복수기의 세정볼 순환펌프

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